Note: Descriptions are shown in the official language in which they were submitted.
2 ~ ~ 7 5 3
The present invention relates to automotive vehicle
seat systems and, more particularly, to lightweight, high
strength, economical frames and recliners employed in such
systems.
Backqround of the invention
Automotive seating systems are typically designed as
part of a host vehicle occupant's protection or safety system.
Accordingly, various requirements are imposed on such seating
systems. They must have high strength and structural
integrity so that the seat remains anchored to the vehicle in
the event of a crash, i.e., the seat tracks should not
separate from the vehicle, from each other or from the seat.
Furthermore, the seat back should either remain in its pre-
crash set position, or under certain conditions collapse in a
predictable, energy absorbing manner. Test results embodied
in U.S. Federal Motor Vehicle Safety Standards 208 and 210
require that the seat belts and their anchorages withstand
loads of 1500 to 3000 pounds without failure. If any
anchorage is mounted to the seat structure, the structure must
withstand such loads as well. The outboard (adjacent the
door) upper and lower seat belts and anchorages should
withstand the load of 1500 pounds and the inboard (adjacent
the center line) lower part should withstand 3000 pounds. In
addition, increased emphasis on fuel economy necessitates
vehicle weight reduction. This, of course, makes it highly
71383-6
WO93/16895 ~ 9 ~ 7 ~ 3 ~ PCT/~S93/0l648
desirable to reduce the weight of the seating system, but mere
weight reduction can adversely impact the strength of the
seating system.
Cost containment is still another requirement
imposed upon automotive vehicle seating systems and prior art
attempts to meet all three requirements, high strength -
lightweight - low cost, have not been satisfactory. Some
attempts have been made to substitute aluminum for steel in
the design of seat frame assemblies. These designs typically
required steel reinforcements to provide the necessary
structural strength and such reinforcements add weight,
package size and cost to the systems.
Another desirable advantage of automotive seating
systems is the integration of the seat restraints or safety
belt means so that the track assemblies, seat and seat belts
are a self-contained unit. If the seat belts were integrated
with seat and track assemblies, adjustment of the seat by the
occupant would not require readjustment of the seat belts.
It would also facilitate the installation of the seat belts
in convertible vehicles where no pillars are readily
available. Usually the seat belts are anchored to the vehicle
body pillar and floor to reduce the loads imposed on the seat
track assemblies during a crash. Attempts to integrate all
of the seat belts with the seat and track assemblies aggravate
the strength and weight considerations noted above.
The use of seat back recliner mechanisms further
aggravate the shortcomings of prior art designs in that they
tend to have an operating range of motion which are limited
to fifty degrees or less. Furthermore, they are configured
to provide the lowest mechanical advantage when the seat back
is in a full down or reclined position wherein an extremely
large motor and drive train is required to lift an occupant
and seat back to the upright position. A dump feature,
necessary to permit entry into the back seat of a two door
vehicle, has proven difficult to provide in seating systems
which include seat back reclining mechanisms. When such dump
features are provided to permit momentary disconnection
between the seat back adjuster and the seat back, "chucking"
i.e., a slight movement of the seat frame and seat back and
7 5 ;~ ~
closeness in construction evident in an unoccupied seat presents a further
problem.
Finally, in so-called fully structural seats in which all three seat belt
anchorage points are born by the seat frame, designs with enhanced strength are
required. However, limited passenger compartment space has made the
packaging of the foregoing features difficult. A related problem results from the
necessity of having a seat frame design which is extremely rigid, particularly when
subjected to frontal impact forces, while collapsing in a controlled, predictable and
energy absorbing manner upon severe rear impact conditions.
Summary of the Invention
The present invention provides a motor vehicle seat recliner
comprising: a lower recliner structure for supporting a seat cushion; an upper
recliner structure including a seat back frame for supporting a seat back, said seat
back frame and said lower recliner structure joined at a hinge point; and an
adjuster mechanism carried by said lower recliner structure engaging said upper
recliner structure for selective, substantially fixed angular positioning
therebetween, said mechanism including a longitudinally disposed drive screw
restrained from rearward displacement by a forward facing thrust surface defned
by said lower recliner structure, a travelling nut threadably engaged upon said
drive screw, an elongated link pivotally connected at one end to said nut and
pivotally connected at an opposite end to a link control bracket, said link control
bracket pivotally connected to said seat back frame at one end and to said link at
an opposite end, whereby when said upper recliner structure is disposed in a
generally upright operating position and upon imposition of frontal impact forces,
71 383-6
~ ~7~
~ said link control bracket positions said link generally parallel with said drive screw
so that said link and a portion of said drive screw intermediate said nut and thrust
surface are subjected to substantially pure compressive loading. This
arrangement provides the advantage of a simple, inexpensive and lightweight
design which exhibits extreme rigidity in frontal impact conditions.
The invention also provides a motor vehicle seat recliner comprising:
upper and lower members joined at a hinge point; and adjuster means for
establishing a substantially fixed angular position between said upper and lower
members, said adjuster means including a linear actuator carried by said lower
10 member operable to selectively displace a carrier member between two fixed
points, a rigid link member pivotally connected to said carrier member, first link
means for interconnecting said upper member and the rigid link member to limit
rotation between said upper and lower members in only one direction, and second
link means for interconnecting said upper member and said rigid link member in
parallel with said first link means and operative to limit rotation between said upper
and lower members in only one opposite direction.
In the preferred embodiment of the invention, the vehicle seat
assembly includes at least two laterally spaced, longitudinally extending lower seat
tracks which are adapted to be rigidly affixed to the floor pan of a host motor
20 vehicle, an upper seat track carried by each of the lower seat tracks for controlled
longitudinal displacement with respect thereto, the upper seat tracks adapted for
supporting a seat pan and cushion. A seat back frame adapted for supporting a
seat back rest is hinged to the two tracks about a common axis. Lastly, an
adjuster mechanism carried by one or both of the upper seat tracks engages the
7 1 383-6
a~ ~ 7 s 3 ~
seat back frame and operates to select and substantially fix the position of the
seat back frame within a range between an upright position and a rearwardly
reclined position. The mechanism includes a longitudinally disposed drive screw
which is restrained from rearward displacement with respect to the upper seat
track by a substantially vertically disposed thrust plate carried on a rearmost end
of the upper track. A travelling nut threadably engaged upon the drive screw is
pivotally linked to one end of a rigid elongated link member. The other end of the
link member is pivotally connected to the seat back frame through an intermediate
control bracket, whereby the link is disposed in a generally parallel relationship
10 with the drive screw when the seat back frame is near its upright position to affect
substantially compressive loading upon the link and a portion of the drive screw
intermediate the nut and the thrust plate. Furthermore, the link is disposed
generally at right angles to the drive screw when the seat back frame is near its
rearwardly reclined position to provide a near maximum mechanical advantage
upon activation of the adjuster mechanism. This arrangement provides a compact
highly efficient seat and seat recliner assembly.
Preferably, the seat recliner includes a latch which is operable to
disengage the adjuster mechanism from the upper recliner structure. This enables
manual free forward rotation or dumping of the upper recliner structure beyond a
20 forward limit of travel established by the adjuster mechanism. This arrangement
allows application of the present invention to two-door vehicles. The latch means
preferably includes a lock plate which is slidingly displaceable between an
engaged position which is abuttingly intermediate the upper recliner structure and
the link and a release position in which the recliner structure is displaceable in one
B 71 383-6
1 7 ~ 3 ~
",;
direction with respect to the link. This arrangement has the advantage of
employing a latch which serves as a dead-bolt and is subjected to purely
compressive loading, providing an extremely strong yet lightweight design.
The lock plate defines a first generally convex surface which is
disposed in a tangentially abutting relationship with a mating surface defined by
the upper recliner structure and a second, opposed generally concave surface
embracingly abutting the link when the lock plate is in the engaged position. The
end of the link is complimentarily shaped to the concave surface to permit limited
sliding engagement therebetween. The first and second surfaces are converging
to effect wedging engagement with the upper recliner structure mating surface and
the link as the lock plate transitions from the release position towards the engaged
position to substantially reduce or eliminate chucking therebetween.
The upper recliner structure includes a seat back frame which is
interconnected to the lower recliner structure by a hinge pin and a link controlbracket which is pivotally connected to the seat back frame at one end and
pivotally interconnected to the opposite end of the link by a pivot pin. This
arrangement provides the advantage of positioning the link so as to ensure
compressive loading during impact while, simultaneously, permitting dumping of
the seat back.
These and other features and advantages of this invention will
become apparent upon reading the following specification, which, along with the
drawings, describes and discloses a preferred embodiment of the invention in
detail.
A detailed description of the disclosed embodiment makes reference
- 5a -
7 1 383-6
to the accompanying drawings. ~ 7
Brief Description of the Drawings
Figure 1, is a perspective, partially cut away view of an automotive
seating system including a fully integrated seat, seat track assembly and seat belt
system;
Figure 2, is a side view of a high strength seat frame from the seat of
Figure 1;
- 5b-
7 1 383-6
CA 02117~31 1999-01-0~
Figure 3, is a top, cross-section view on an
enlarged scale of the seat frame assembly taken on lines III
- III of Figure 2;
Figure 4, is a cross-section view taken on lines VI
s - VI of Figure 3 on an enlarged scale with the latch lock
plate in the engaged position;
Figure 5, is the cross-section in partial relief of
Figure 4 but with the lock plate moved toward the release
position;
Figure 6, is the cross-section in partial relief of
Figure 4 with the seat back frame adjusted to its full upright
position;
Figure 7, is the cross-section in partial relief of
Figure 4 with the seat back frame rotated to its fully
lS reclined position;
Figure 8, is a top plan view of the seat back frame
of the present invention;
Figure 9, is a front cross-section view taken on the
lines IX - IX of Figure 8;
Figure 10, is a side, broken cross-section view
taken on lines X - X of Figure 9;
Figure 11, is a cross-section view of the track
assembly taken on lines XI - XI of Figure 5 on an enlarged
scale;
Figure 12, is a rear view of the lower recliner
structure on an enlarged scale; and
Figures 13 - 22, illustrate various steps in forming
the seat back frame.
Detailed Description of the Preferred Embodiment
Referring to Figure 1, an integrated automotive
seating system 10 includes an automotive seat 12, a pair of
seat track assemblies 14 and a seat belt system 16. Each
track assembly 14 includes a lower track member 18 adapted for
use with conventional fasteners to secure it to the floor of
an associated host vehicle and also includes an upper track
member 20 adapted for use with conventional fasteners to
secure it to the bottom of the seat 12. The track members 18,
20 are
7 5 ~ ~
~~elongated extrusions made of lightweight, high strength
material such as an aluminum alloy and are formed so that they
are slideably engaged with each other for longitudinal
movement of the upper track member 20 and seat relative to the
fixed lower track member 18. A conventional coupling
arrangement is associated with each upper track member 20 to
assure that they move in unison. Accordingly, the position of
the seat 12 is adjustable longitudinally in the vehicle.
Although not shown in the drawing, each seat track
assembly is also associated with locking means to lock the
upper seat track member 20 in an adjusted position. If seat
adjustment is accomplished manually, any conventional such
locking means can be used. Preferably, the seat track
assemblies are associated with an electric motor and drive
means to drive the upper seat track 20 for adjusting its
position. Any conventional motor and drive means can be
utilized and as usually in such arrangements, the locking
means is part of the motor and drive means.
The automotive seat 12 includes a lightweight high
strength frame 32. It also includes a bottom cushion 21 and
back rest 22. Embedded with the top of back rest 22 is an
anchor member 24 which holds a shoulder belt 26 of the seat
belt system 16. The track assemblies 14 also each includes an
anchor member 28 and each anchor member holds a portion of a
lap belt 30. All cooperate in a conventional manner to hold
the occupant in the seat 12 in the event of a crash. For the
sake of simplicity, structural details of the seat pan, cross
braces and vertical and longitudinal seat adjuster mechanisms
are deleted. Typical prior designs can be found, by way of
-- 7
71383-6
, ~
~ o
2 ~
~example, in U.S. Patents 4,432,583 and 4,015,812.
Referring to Figure 11, the construction of track
assemblies 14 is shown in greater detail. Each track assembly
14 is essentially the same and, accordingly, only one need to
be shown and described.
- 7a -
71383-6
CA 02117~31 1999-01-0
Referring to Figures 2 through 5, the structural
detail of the seat frame 32 is illustrated which includes an
upper member or recliner structure shown generally at 34 and
a lower member/recliner structure generally at 36 joined at
a pivot or hinge point 38. All major structural elements are
formed of high strength aluminum alloy.
Lower recliner structure 36 comprises upper and
lower track members 18, 20, inner and outer recliner pivot
supports 42, 44, respectively, and a thrust plate 46. Upper
track member 20, pivot supports 42 and 44 as well as thrust
plate 46 are constructed as a single rigid integrated assembly
such as by welding and/or threaded fasteners 48. In the
preferred embodiment, welding is avoided or minimized,
especially on the track members due to its tendency to
metallurgically weaken the material. Thrust plate 46 and
pivot supports 42, 44 can be formed from a single piece of
material and configured in a generally U-shape (as viewed from
above). As illustrated, pivot supports 42, 44 are formed
separately and include inwardly turned flanges 41 and 43 which
are butt welded and define laterally extending goblet-shaped
extensions 45 and 47 which, in assembly, are captured within
an upwardly opening channel 58 formed by the upper track
member 20 to help prevent release thereof. The uppermost
portions of pivot supports 42, 44 form registering apertures
49, 51, respectively, for receiving a large steel pivot pin
50 which is held in assembly by deformation, fasteners or
other suitable means.
As best viewed in Figures 2, 3 and 12, thrust plate
46 is formed of extremely heavy gauge material and is rigidly
mounted to prevent separation from the upper track member 20
under high loading conditions by six hardened bolts 48a-f
extending through an array of bores 53a-f and threadably
engaging corresponding longitudinally extending passageways
20a-f defined by bosses 20a-l integrally extruded in upper
track member 20. Plate 46 has two laterally centered through
bores 52, 54 formed therein. The surface portion of plate 46
defining bores 52 and 54 facing forwardly in application
toward the front of the host vehicle (leftwardly as viewed in
Figures 2 through 7), is deemed a thrust surface 56.
_. _
W093/l6895 Ci~ 2 1 1 7 5 3 1 PCT/US93/01648
As best seen in Figure 11, upper track member 20 is
generally H-shaped in the cross-section, defining upwardly and
downwardly opening longitudinally extending channels ~8 and
60, respectively. Drive screws 62 and 64 are disposed within
channels 58 and 60, respectively, and are each individually
driven by a motor/gear transmission 66, 68, respectively,
carried by upper track member 20 in the usual manner.
Motor/gear transmissions 66, 68 are selectively energized by
the vehicle operator via a power control circuit (not
illustrated) to effect reclining of seat back 34 and the
longitudinal positioning of seat 12, respectively. The
rearward most (rightward) ends of drive screws 62, 64, have
steps 70, 72 formed therein rightwardly abutting thrust
surface 56 and extending through bores 52, 54, respectively.
C-clips 182, 183 or other suitable fasteners are applied in
radially outwardly opening circumferential grooves to axially
restrain drive screws 62 and 64 from leftward displacement.
Thus, drive screws 62 and 64 are carried for displacement with
upper track member 20 but are selectively rotatable in
response to an operator input. Drive screw 64 carries a
traveling nut (not illustrated) which is interconnected with
lower track member 18 through linkage as is well known in the
art to effect longitudinal adjustment of seat 12.
Upper structure 34 constitutes a seat back frame 73
made from an inverted, generally U-shaped tube formed of high
strength material such as aluminum alloy. The U-shaped
portion of the upper structure is formed from a single piece
of aluminum tube that is either extruded with a varying wall
thickness or, preferably, double-butted (rolling and working)
a constant diameter and constant wall thickness tube to
produce a variable thickness wall. In either event, the
resulting tube form varies in wall thickness from a maximum
of approximately 4.5 millimeters to a minimum of 2.5
millimeters. As viewed in Figures 8 through 10, the seat back
frame 73 comprises inboard and outboard vertically extending
leg members 74 and 76, interconnected by a generally
horizontal base member 78. A laterally disposed reinforcement
member 80 bridges the free ends of leg members 74 and 76 to
provide structural integrity and is affixed thereto by welding
WO 93tl689~ PCI/~,'S93/01648
'CA2'1~' 75:3~ lo
or other suitable fastening means. The portion of leg members
74 and 76 below reinforcement member 80 are of relatively
thick constant wall section to enhance strength at the point
of mounting upon lower structure 36 while the section of the
tubing above reinforcement member 80 tapers down to a thinner
gage to reduce overall weight and lower the center of gravity
of the assembly. The central portion of base member 78 has
a flattened portion 82 to facilitate mounting of a headrest
83 (Figure 1) in the final trimmed seat assembly. The upper
portions of leg member 74 and 76 are generally circular in
cross-section and transition into a flat sided oval shape at
the lowermost end thereof as best seen Figures 3 and 8.
Reinforcement member 80 is curved to accommodate contours of
the occupant's back for comfort and is attached to leg members
74 and 76 at their neutral stress axis.
A vertically elongated aluminum strap brace 84 is
rigidly fastened at the lower end thereof to reinforcement
member 80 and, at the upper end thereof supports anchor member
24. Strap brace 84 is secured to anchor member 24 and
reinforcement member 80 by blind rivets 107 or other suitable
fasteners. Shoulder belt 26 extends from anchor member 24
behind base member 78 and over the occupant's shoulder. Thus,
frontal impact induced forces will place strap brace 84 in
pure tension. As a result, relatively thin material can be
employed allowing anchor member 24 to longitudinally float
within the back rest 22 padding as indicated by arrow 85 to
facilitate occupant comfort.
Opposed seat back dump handles 86 and 88 are
pivotally mounted to brackets 90 and 92, respectively, carried
within the upper part of leg members 74 and 76, respectively,
of seat back frame 73. The handles 86 and 88 are
interconnected by wires 94 and 96 and extend laterally in
opposite directions to provide occupant access from either
side of seat 12. Guide wires 94 and 96 pass through guide
holes 91 and 97, and 93 and 95, respectively, formed in leg
members 74 and 76. A control wire 98 extends from handle 88
to the open bottom end of leg member 76 to affect dumping of
seat back frame 73 upon lifting of the exposed portion of
either handle 86 or 88, as indicated by arrows 100 and 102.
CA 02117~31 1999-01-0~
Handles 86 and 88 extend through vertical slots 104 and-106
in the wall of leg members 74 and 76, respectively. For the
sake of simplicity, seat system 20 is described herein as
including a power seat back recliner only on the outboard
portion thereof. As will be described in detail hereinbelow,
control wire 98 is operatively connected with said recliner.
It is contemplated that if required, dual recliners can be
employed. In such case~ a second control wire (not
illustrated) would be interconnected from handle 86 to the
inboard recliner mechanism within leg member 74.
An important aspect of the design of seat back frame
73 stems from its A-shaped profile transitioning from a small
longitudinal dimension (approximately 6.4cm) near its top to
a greater dimension (approximately 8.7cm) adjacent the bottom
ends of leg members 74 and 76. This feature is believed to
substantially increase the overall structural integrity of
frame 73 without adding significant cost or weight thereto,
and also provides greater room between the sides of the seat
back frame 73 for the occupant.
The bottom ends of leg members 74 and 76 form
openings 108 and 110 and define a vertically tapered (from
front to rear) end surface 112 to provide clearance for the
seat back hinge and recliner mechanism. Openings 108 and 110
provide access to a cavity 114 within frame 73. The inner
surface of the longitudinally forward most wall portion of leg
members 74 and 76 define an abutment surface 116 adjacent each
opening 108 and 110. Large, registering lateral through bores
118 and 120 are formed near openings 108 and 110,
respectively. A second pair of smaller, laterally extending
registering through bores 122 and 124 are formed slightly
beneath bores 118 and 120.
Referring to Figures 4 through 7, the structural
details and operation of seat recliner/back adjuster 40 is
illustrated. Back frame 73 is pivotally mounted to pivot
supports 42 and 44 by pivot pin 50 which extends throush
registering bores 52, 54 and 120 (118) and is secured in
assembly as best illustrated in Figure 3 and described
hereinabove. As mounted, seat back frame 73 is rigidity
restrained in assembly with lower recliner structure 36 and
CA 02ll7~3l l999-Ol-0
12
is permitted only a limited degree of relative rotation
therebetween. A solid cylindrical traveling nut 12 6 has a
threaded through bore 128 engaged upon drive screw 62 for fore
and aft longitudinal translation therealong. A generally
U-shaped elongated link 130 has laterally spaced inner and
outer legs 132 and 134, respectively integrally interconnected
by a base 136. Legs 132 and 134 laterally straddle drive
screw 62. Registering through bores 138 and 140 are formed
adjacent one end of legs 132 and 134, respectively, and
establish a slip-fit with the lateral ends of traveling nut
126 whereby the end of link 130 associated with bores 138 and
140 is free for relative rotation with respect to nut 126 but
is longitudinally drivingly positioned thereby. A smaller
diameter bore 142 extends laterally through an opposite end
of link 130. A link control bracket 144 is generally U-shaped
to embrace the lowermost leading outer-surface of leg member
76. Bracket 144 has a pair of large bores 146 formed therein
which register with bores 120 of leg member 76 and receive
pivot pin 50 therethrough. As best viewed in Figure 4,
bracket 144 extends downwardly from its point of pivotal
attachment to seat back frame 73 wherein upon clockwise
rotation of seat back frame 73 from its illustrated position,
bracket 144 will tend to be carried therewith. Conversely,
upon counterclockwise rotation of seat back frame 73 from its
illustrated position in Figure 4, bracket 144 will tend to
remain in its illustrated position. The lowermost portion of
bracket 144 has a set of registering bores 148 formed therein
which are positioned in alignment with bore 142 of link 130
and joined therewith by a connecting pin 150, such as a
hardened steel roll pin, to establish a pivot joint. The
left-hand most surface of the end 136 of link 130 associated
with bore 142 is generally convex and forms an abutment
surface 152.
A lock plate 154 has a lateral through bore 156
formed in the upper right-hand corner (as viewed in Figure 4)
as well as a vertically extending arcuate slot 160 laterally
extending therethrough in the middle portion thereof. Lock
plate 154 is retained in assembly by a laterally extending
guide pin 162 extending through bores 124 (122) of leg member
W O 93t16895 CA21 17531 ~ PC~rJ~S93/01648
'- 13 ~ ' 9'' ~ ~b
76 (74) as well as slot 160. A generally triangular lock
release crank member 164 formed of injection molded
polypropylene is disposed within cavity 114 and includes a
laterally extending through bore 166, 168 and 170 adjacent
each corner thereof. Bore 166 is dimensioned for slip-fit
receipt of pivot pin 50. Bore 168 fixedly receives the
lowermost end of control wire 98. as well as one end of a
tension spring 171. The other end of spring 171 is hooked to
the end surface 112 of leg member 76. Spring 171 continuously
urges crank member 164 toward the position illustrated in
Figure 4. The remaining corner of crank member 164 is loosely
disposed within a vertical slot 172 formed in lock plate 154,
exiting upwardly and rightwardly therefrom. A guide pin 174
extends laterally through bores 156 of lock plate 154 and bore
170 of crank member 164.
As assembled, crank member 164 is restrained within
cavity 114 but is free for rotation about the axis of pivot
pin 50 between limits of travel established by the length of
slot 160 within lock plate 154. The interconnection between
lock plate 154 an~ crank member 164 as well as the
interconnection between link control bracket 144 and link 130
comprise clevis joints.
The left-hand most edge of lock plate 154 is curved
and generally convex to define an abutment surface 176
disposed adjacent surface 116 of leg member 76. The lower
right-hand corner of lock plate 154 has a concave recess
formed therein to define a further abutment surface 178.
Abutment surfaces 152 and 178 are substantially complimentary
and have nearly constant radiuses whereby when lock plate 154
is in the position illustrated in Figure 4, a large surface
area contact is established therebetween. Furthermore,
limited relative rotation between surfaces 152 and 178 is
permitted.
As viewed in Figure 4, lock plate 154 is disposed
in the locked or engaged position in which surface 116 abuts
surface 176 and surface 152 abuts surface 178, virtually
eliminating chucking between the seat back frame 73 and the
lower recliner structure 36. In this position, control wire
98 tends to be slack and the spring 171 biasing crank member
.,~ "
CA 02117~31 1999-01-0~
164 tends to push lock plate 154 downwardly. Surfaces 176 and
178 are tapered downwardly to create a wedging affect to
eliminate any looseness or play that may occur over time due
to wear or deformation. In this position, pin 162 is nearly
(but still slightly spaced from) the top of slot 160. So
positioned, the seat back frame 73 is rigidly connected to the
lower recliner structure 36 in both directions of rotation
about pin 50. In effect, bracket 144 and lock plate 154 are
disposed in parallel between frame 73 and link 130, bracket
144 tensionally resisting rotation in one direction only and
link 130 compressively resisting rotation in an opposite
direction only. When forces, such as an occupant leaning into
the back rest 22, tend to displace seat back frame 73
clockwise about pin 50, the leading external surface of leg
member 76 is captured by bracket 144 which, in turn, is
restrained by link 130, which, in turn, is restrained by
traveling nut 126, which is restrained by drive screw 62 which
is axially restrained by suitable fastening means such as
screws 180 associated with motor/gear transmission 66 as well
as C-clip 182. The provision of axial and radial support to
drive screw 62 at both ends thereof greatly enhances
structural integrity of the adjuster as well as allows an
approximately 50% reduction in the axial length of drive screw
62 without diminishing the range of motion of the upper
structure 34 as contrasted with prior art designs in which the
carrier nut is fixed to the upper track member and the drive
screw reciprocally axially translates with respect thereto.
Seat back frame 73 as well as upper and lower track
members, 20 and 18, respectively, are preferably constructed
of a high strength lightweight material such as aluminum
alloy. Materials with a yield strength of approximately
50,000 psi such as 2000, 6000 or 7000 series aluminum alloys
are preferred. Link control bracket 144, link 130, and
traveling nut 126 are also constructed of aluminum alloy.
Drive screw 62 and connecting pin 150 are constructed of steel
or other suitable material. The illustrated arrangement has
been found to meet typical customer provided loading
requirements as well as government mandated crash worthiness
specifications for both front and rear impact loading. Under
CA 02117531 1999-01-0~
rear loading conditions, bracket 144, link 130 and the portion
of drive screw 62 intermediate traveling nut 126 and C clip
182 are subjected almost entirely to tensile loading in the
present design. When rear impact loading substantially exceed
nine to ten thousand inch pounds, the brackets and links will
deform reasonably predictably to provide energy absorption as
the seat back and occupant rotate rearwardly. As should be
apparent upon reading of the specification, selection of
material and component geometry can readily provide variation
lo of the acceptable torque limit about pivot pin 50 and energy
absorption characteristics of seating system 10.
When subjected to frontal impact or loading, the
seat back frame 73 will tend to rotate counterclockwise as
indicated by arrow 184 about pivot pin S0. Under such
conditions, it is desirable to retain the seat back frame 73
in its pre-impact positional setting and thereby avoid
displacement of any of the seat belt anchor members
(especially 24) to ensure that belt tensioning remains in
effect throughout the crash event. Lap belt 30 anchor members
28 are affixed to pivot supports 42 and 44 by hardened bolts
186 and nuts 188 extending through laterally registerinq
apertures 190 and 192 formed in pivot supports 42 and 44,
respectively. Bolt 186 also adds strength to lower recliner
structure 36. Upon frontal impact, surface 116 of leg member
76 is thrust rightwardly against surface 176 of lock plate
154. Lock plate 154 is i m~ ately captured in its
illustrated position inasmuch as the surface 178 embracingly
engages surface 152 of link 130 and cannot be removed from its
latched position as long as frontal impact loading on the seat
back frame 73 is taking place. Thus, the force moment arm
created by an impact is transferred from the seat back frame
73 through lock plate 154, link 130, traveling nut 126 and the
portion of drive screw 62 intermediate traveling nut 126 and
thrust plate 46. Due to the pivot joints, the lock plate 154,
link 130, and drive screw 62 are subjected to substantially
pure compressive loading in this case. To the extent they
exist, off axis forces are distributed over a large area of
surface contact between link 130 and drive screw 62 with
negligible effect. The applicant has found a loading
CA 02ll7~3l l999-Ol-0
16
tolerance up to 90,000 inch pounds with the present design.
Inasmuch as virtually all of the moment arm forces from
frontal impact loading are directed axially through the
rearmost end of drive screw 62, it is critical that thrust
plate 46 be securely retained upon the rear end of upper track
member 20.
Under normal operating conditions, to effect a
dumping of the upper recliner structure 34 and back rest 22,
either handle 86 or 88 is raised as indicated by arrows 100
and 102, respectively, which, in turn, will produce a tension
on control wire 98 as indicated by arrow 185 in Figure 5.
Under such conditions and when the seating system 10 is not
subject to significant levels of de-acceleration, crank member
164 will freely rotate counterclockwise about pivot pin 50
thereby raising lock plate 154 from its engaged position
illustrated in Figure 4 to its released position wherein guide
pin 162 contacts the lowermost end of slot 160. Figure 5
illustrates the transition of lock plate 154 as it is nearing
but has not yet achieved its release position. When in the
20release position, lock plate 154 is elevated above link 130
and seat back frame 73 is free to be rotated counterclockwise
as indicated by arrow 184 to effect dumping of the seat back.
One advantage of the present invention is that the
adjuster means 40 has a memory whereby when the seat back
frame 73 is returned from its dumped position to its pre-set
upright position, it will remember the setting prior to the
dumping process, inasmuch as link 130 has not moved.
Furthermore, the resetting process will displace the lock
plate 154 from its release position back to its engaged
position illustrated in Figure 4 with a sufficient degree of
over-travel to ensure that any looseness or lost motion is
eliminated.
The seat back frame 73 is illustrated in Figures 4
and 5 set in a nominal or design setting intermediate the
rotational limits of travel which it may achieve with the
present design over approximately 75 degrees between a full
upright setting as illustrated in Figure 6 in a fully reclined
position as illustrated in Figure 7. As motor/gear
transmission 66 is selectively energized by the operator,
WO93tl689~ C A ~ 1 PCT/~'S93/01648
17
drive screw 62 will rotate in one direction or the other to
effect longitudinal translation of traveling nut 126 from its
rearward most limit of travel illustrated in Figure 6 to its
forward most limit of travel illustrated in Figure 7. Nut 126
is prevented from rotation about the axis of drive screw 62
by its engagement wi~h link 130. Stops are established when
link 130 contacts thrust surface 56 of thrust plate 46 at one
limit of travel and motor/gear transmission 66 at the other
limit of travel. When the seat back frame 73 is in or near
its upright most position, link 130 embraces drive screw 62
along its entire length whereby an imaginary line drawn
between the axis of traveling nut 126 and pin 150 approximates
(approximately 15 degrees offset) becoming parallel to the
axis of drive scre~ 62. This arrangement, in addition to
imposing front impact induced forces axially upon drive screw
64, has a further benefit in that the minimum mechanical
advantage of the seat back recliner mechanism is achieved when
the seat back is in its uppermost position and will be
assisted in its operation by both gravity and the forces
imposed by an occupant of seat 12. Conversely, when the upper
recliner structure 34 is in its fully reclined position as
illustrated in Figure 7, the imaginary line drawn between the
axis of traveling nut 126 and connecting pin 150 are generally
perpendicular to the axis of drive screw 62 to provide maximum
mechanical advantage during early stages of displacement from
the illustrated fully reclined position toward the upright
position. Restated, a second imaginary line extending between
the axes of pivot pin 50 and guide pine 162 will be offset -
15 degrees (from vertical) as shown in Figure 6 and +60
degrees as shown in Figure 7. These measures are, of course,
design specific and will change as modifications are
implemented. They are presented here only as an example.
A further advantage of the present design is
apparent upon reference to drawing Figure 2 wherein virtually
the entire adjuster mechanism 40 is enclosed either within the
upper channel 58 of upper track member 20 or within tubular
seat back frame 73 lending for a very clean, compact and
easily packaged design.
WO93/16895 PCT/~'S93/01648
a9 ~53 ~ ~ 18 ~
Referring to Figures 13 through 22, the various
steps employed in forming the seat back frame 73 are
illustrated. Although the complex shape of frame 73 could be
drawn in a variable geometry extrusion die or possibly cast
to net shape, the preferred approach is to start with a
conventionally extruded metal tube as illustrated in Figures
13 and 14 having a substantially constant nomi~al diameter (d)
and gauge or wall thickness (t). The extrusion is trimmed to
a predeter~ined length (l) to form a tube blank 194 having
open ends 196 and 198 and a middle portion, designated 200,
intermediate said ends.
Referring to Figures 15 and 16, the next step in the
method is to re-extrude or mechanically work tube 194 such as
by ~'double butting", hydraulic reduction or other suitable
mechanical process which results in varying the wall thickness
(t) to establish a thickness profile along length (l) of tube
194. In the preferred embodiment of the present invention,
the wall thickness profile has five distinct regions. In two
end regions 202 and 204, wall thickness assumes a maximum
value (tmax) which is constant throughout the region. A
middle region 210 generally centered in tube 194 in the middle
portion 200 thereof has a wall thickness that assumes a
minimum value (tmin) which is constant throughout.
Intermediate end regions 202 and 204 and middle region 210 are
two transition regions 206 and 208 in which the characteristic
wall thickness (t) tapers from tmaX to tmin. Although on the
preferred embodiment, tube 194 is symmetrical about its
centerline (cl), it is contemplated that in seat frames only
employing a single recliner mechanism, an end region and
transition region as described hereinabove maybe formed only
on one end of tube 194 and the other tube end remains at a
tmin dimension.
Referring to Figures 17 and 18, the next step in the
method is that of forming two substantially right angle
corners 212, 214 within the middle region 210 of blank 194,
whereby the blank assumes a generally inverted U-shape. The
bending is preferably accomplished by press or punch bending
processes well known in the art.
WO93/16895 ~ 3 1 PCT/~'S93/01648
-
19
Referring to Figures 19 and 20, the next step in the
method involves the forming of blank end regions 202 and 204
into flat sided ellipsoid sections having maximum dimension
axes (a-a) which are substantially parallel to one other. By
r'flat sided," it is meant that a substantial portion of the
longitudinally extending sides (s) are sufficiently planar to
ensure stabilizing surface contact with pivot supports 42 and
44 (through intermediate link control bracket 144) as is best
viewed in Figure 3.
Referring to Figures 21 and 22, a last step involves
forming registering pivot pin 50 receiving bores 118 and 120
as well as guide pin 162 receiving bores 122 and 124 as
described with reference to the foregoing description with
respect to drawing Figures 9 and 10. Bores 118 through 124
are formed in end regions 202 and 204. This step also
includes the attachment of reinforcement number 80 to facing
mounting locations 216 and 218 within end regions 202 and 204.
Mounting locations 216 and 218 straddle a characteristic zero
load line (zll). Attachment of reinforcement member 80 is
accomplished by welding as close as possible to the zero load
line or the use of other suitable fasteners. At this time,
additional contours are formed in blank 194 to produce seat
back frame 73 as described hereinabove. Such deformation
includes forming of flattened portion 82, slots 104 and 106,
guide holes 91, 93, 95 and 97 as well as the contours of end
surfaces 112 as best viewed in Figure 10.
Reinforcement member 80 is preferably formed of
constant gauge high strength aluminum alloy material which is
mechanically worked into its illustrated configuration and has
a gauge approximately equal to the maximum thickness tmaX of
the end regions 202 and 204 of blank 194.
In carrying out the foregoing forming methodology,
it is recognized that various well-known metal working
processes may be employed. For example, tube 1~4 can first
be annealed, preferably to an "0" or "W" temper prior to
working. Furthermore, age and work hardening of aluminum is
also well-known. Shaping of the blank using a mandrel or
other similar tube forming techniques is also contemplated.
WO93/16895 ~A21 1 7531 PCr/US93/0164~
For the sake of brevity, the specifics of such known
methodologies is deleted here inasmuch as they are adequately
described in numerous treatises.
It is to be understood that the invention has been
described with reference to a specific embodiment to provide
the features and advantages previously discussed and that the
embodiment is susceptible of modification as will be apparent
to those skilled in the art. For example, although the
present invention is principally intended for application in
bucket or split-bench type seats, in the broadest sense, it
could be employed in full bench, multi-passenger seats as
well. The high strength seat back frame described could also
be employed in fixed back type seats and the method steps
could be performed in a different order. Accordingly, the
foregoing is not to be construed in a limiting sense.
